WO2017047772A1 - Roulement à billes à contact angulaire - Google Patents

Roulement à billes à contact angulaire Download PDF

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Publication number
WO2017047772A1
WO2017047772A1 PCT/JP2016/077500 JP2016077500W WO2017047772A1 WO 2017047772 A1 WO2017047772 A1 WO 2017047772A1 JP 2016077500 W JP2016077500 W JP 2016077500W WO 2017047772 A1 WO2017047772 A1 WO 2017047772A1
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WO
WIPO (PCT)
Prior art keywords
ball bearing
diameter surface
cage
angular ball
inner ring
Prior art date
Application number
PCT/JP2016/077500
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English (en)
Japanese (ja)
Inventor
裕士 恩田
Original Assignee
Ntn株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Ntn株式会社 filed Critical Ntn株式会社
Publication of WO2017047772A1 publication Critical patent/WO2017047772A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/38—Ball cages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/64—Special methods of manufacture
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings

Definitions

  • the present invention relates to an angular ball bearing used for supporting a spindle of a machine tool.
  • angular ball bearings can receive a combined load composed of a radial load and a relatively large axial load. For this reason, it is often used for applications such as machine tools, medical equipment, construction machines, and agricultural machines that require high-speed rotation even under environments with heavy loads and various load directions.
  • Angular contact ball bearings that support machine tool spindles are required to rotate stably and at high speeds in order to increase machining efficiency.
  • Oil mist lubrication, air-oil lubrication, and bearings that supply lubricating oil from the outside are required for lubrication.
  • Grease lubrication that encloses grease inside is used.
  • coolant is supplied to the workpiece and the cutting tool in order to lubricate and cool the workpiece and the cutting tool during cutting.
  • coolant liquid or foreign matter enters the angular ball bearing that supports the spindle of the machine tool, it may affect bearing lubrication and cause bearing seizure.
  • the seal structure at the front end of the main shaft has been devised, but it may still enter the bearing and cause problems.
  • Angular ball bearings that support high-speed operation spindles, such as machine tool spindles, generate a large amount of heat during high-speed operation and increase rotational torque. Therefore, the seal structure is often a non-contact type.
  • Patent Document 1 proposes a sealed angular contact ball bearing that prevents heat generation due to contact between an inner ring seal groove and a seal lip.
  • the angular ball bearing 11 includes an inner ring 12, an outer ring 13, a ball 14, and a cage 15, and includes a pair of seals 16 and 16 that seal the end of the bearing space between the inner and outer rings.
  • the seal lip 16a of the seal 16 is fitted in a seal mounting groove provided in the outer ring 13, and the inner ring 12 of the inner ring seal groove 12a is positioned in the annular inner ring seal groove 12a provided on the outer diameter surface of the inner ring 12.
  • the distance between the inner surface on the end surface side and the side surface of the seal lip 16a is a distance at which the seal lip 16a and the inner ring seal groove 12a are held in a non-contact manner.
  • An angular ball bearing 21 shown in FIG. 6 includes an inner ring 22, an outer ring 23, and a ball 24, and the ball 24 is held by a T-shaped cage 25.
  • the flange portion 25a of the cage 25 is arranged on the wide opening side (counter bore side) of the angular ball bearing to suppress the entry of coolant liquid or foreign matter into the rolling portion.
  • the angular contact ball bearing with seal shown in FIG. 5 and the angular contact ball bearing having the T-shaped cage shown in FIG. 6 have a space limitation in the bearing width direction, and the ball (ball) is small or the load capacity is increased.
  • the ball (ball) is small or the load capacity is increased.
  • the T-type cage tends to collect grease near the ball. If grease accumulates excessively in the vicinity of the ball, it takes time for the break-in operation, and there is a possibility of rapid temperature rise or burning due to re-engagement of grease during operation.
  • the present invention has been made to cope with such problems, and does not require a space in the bearing width direction for the seal, can increase the load capacity, and can prevent the entry of coolant liquid or foreign matter.
  • An object of the present invention is to provide an angular ball bearing that can be suppressed.
  • An angular contact ball bearing according to the present invention is an angular contact ball bearing comprising an inner ring and an outer ring that are raceways, a plurality of balls interposed between the inner and outer rings, and a cage that holds the balls. At least one of the outer diameter surface of the cage and the inner diameter surface of the outer ring facing the outer diameter surface, and at least one of the inner diameter surface of the cage and the outer diameter surface of the inner ring facing the inner diameter surface And having a flocked portion formed by flocking fibers.
  • the angular ball bearing is an inner ring rotary bearing, and the flocked portion is formed on the outer diameter surface of the cage and the outer diameter surface of the inner ring.
  • the inner ring or the outer ring is provided with a counter bore on one side of the raceway groove, and the flocked portion is formed at an axial position on the counter bore side with respect to the ball in each member. Moreover, the said hair transplant part is formed in the width surface of the said holder
  • the above-described flocked portion is composed of a plurality of types of fibers having different fiber lengths. Further, the fiber is a synthetic resin fiber, and the flocked portion is an electrostatic flocked portion.
  • the angular ball bearing of the present invention comprises an inner ring and an outer ring that are raceways, a plurality of balls interposed between the inner and outer rings, and a cage that holds the balls.
  • This angular ball bearing is an inner ring rotary bearing, and the flocked portion is formed on the outer diameter surface of the cage and the outer diameter surface of the inner ring. It is possible to suppress the coolant liquid and foreign matter from entering the rolling portion from the gap between the vessels or the gap between the inner ring and the cage.
  • the inner ring or the outer ring is provided with a counter bore on one side of the raceway groove, and the flocked portion is formed at an axial position on the counter bore side with respect to the ball in each member. Can seal the wide opening side.
  • the flocked portion is also formed on the width surface of the cage, the area of the flocked portion is widened, so that more coolant liquid and foreign matter entering from the outside of the bearing can be adsorbed, and the intrusion into these rolling portions Can be suppressed.
  • the flocked portion is composed of a plurality of types of fibers having different fiber lengths.
  • the fiber is a synthetic resin fiber and the flocked portion is an electrostatic flocked portion, swelling and dissolution due to oil hardly occur and it is chemically stable and becomes a homogeneous and dense flocked portion.
  • FIG. 1 is a partial cross-sectional view of an angular ball bearing having a flocked portion (cage outer diameter surface, inner ring outer diameter surface) as an angular ball bearing of the present invention.
  • a plurality of balls 4 are arranged in a circumferential direction in a raceway space between an inner ring 2 and an outer ring 3, and the inner ring 2, the outer ring 3, and the balls 4 have a predetermined contact angle. It is provided with ⁇ .
  • These balls 4 are held at equal intervals in the circumferential direction by a cage 5.
  • the cage 5 is a resin-made machined cage, and pocket portions for holding the balls 4 are provided at regular intervals in the circumferential direction in an annular cage body.
  • a counter bore whose inner diameter is gradually increased outward is provided on one side (right side in the drawing) of the raceway groove.
  • the counter bore having only the outer ring is described, but the same applies to the case where the inner ring is provided with the counter bore.
  • the cage 5 is an outer ring guide system, and is guided to the outer ring 3 by a part of the outer diameter surface (left side in the figure) of the cage 5 coming into contact with the inner diameter surface of the outer ring 3.
  • This angular ball bearing 1 is an inner ring rotary bearing in which an outer ring 3 is fixed to a housing or the like, and an inner ring 2 rotates together with a support target member such as a machine tool main shaft. Further, the angular ball bearing 1 does not use a seal member.
  • the type of lubrication is air oil lubrication or oil mist lubrication that constantly supplies lubricating oil from the outside of the bearing to the inside of the bearing. Moreover, it is good also as grease lubrication formed by enclosing grease.
  • fibers are applied to (1) the outer diameter surface 5a of the cage 5 and (2) the portion of the outer diameter surface 2a of the inner ring 2 that faces the inner diameter surface 5b of the cage 5.
  • a flocked portion 6 formed by flocking is formed.
  • the flocked portion 6 is formed on the collar portion (ring portion) of the cage 5, which is the portion facing the non-orbital portion of the outer ring 3, of the outer diameter surface 5 a of the cage 5.
  • the flocked portion 6 is formed in a portion of the outer diameter surface 2 a of the inner ring 2 that faces the inner diameter surface 5 b of the collar portion (ring portion) of the cage 5.
  • the flocked portions 6 of (1) and (2) are arranged at the same position in the axial direction on the counterbore side.
  • all the hair transplant parts of (1) and (2) are formed continuously or intermittently in the circumferential direction.
  • the short fibers constituting the flocked portion 6 have a single fiber length, and the length is approximately the same as the gap (clearance) between the members at the formation locations.
  • the flocked portion 6 expands in the outer diameter direction due to the centrifugal force during rotation of the bearing, the flocked portion 6 in (1) passes through the gap between the outer ring 3 and the cage 5, and the flocked portion 6 in (2) Each gap with the cage 5 is sealed. Thereby, it can suppress that coolant liquid and a foreign material penetrate
  • FIG. 2 is a partial cross-sectional view of an angular ball bearing having a flocked portion (cage outer diameter surface, inner ring outer diameter surface) as an angular ball bearing of the present invention.
  • a flocked portion 6 formed by flocking fibers is formed in a portion facing 5b.
  • a plurality of types of fibers having different fiber lengths are used as the short fibers that form the flocked portion 6.
  • the other overall configuration is the same as that of the angular ball bearing of the form shown in FIG.
  • the flocked portion 6 has its fiber tip in sliding contact with the inner diameter surface 3 a of the outer ring 3, and the (2) flocked portion 6 has its fiber tip in sliding contact with the inner diameter surface 5 b of the cage 5. Since this sliding contact increases torque and heat generation, it is necessary to suppress this. For example, by adjusting the fiber length so that it is about the same as each gap, the contact becomes light contact, and an increase in torque can be prevented.
  • the outer ring 3 and the cage 5 are used by using fibers having the same fiber length as the gaps and fibers having a fiber length shorter than the gaps.
  • short fibers do not contact, and long fibers become light contact, and an increase in torque and heat generation can be suppressed.
  • it has sufficient sealing property by the flocking structure which combined these.
  • FIG. 3 is a partial cross-sectional view of an angular ball bearing having a flocked portion (outer ring inner diameter surface, cage outer diameter surface, cage inner diameter surface, inner ring outer diameter surface) as an angular ball bearing of the present invention.
  • a flocked portion 6 formed by flocking fibers is formed on the inner diameter surface 5 b of the cage 5.
  • the flocked portion 6 is formed in a portion of the inner diameter surface 3 a of the outer ring 3 that faces the outer diameter surface 5 a of the collar portion (ring portion) of the cage 5.
  • the flocked portion 6 is formed on the collar portion (ring portion) of the cage 5 which is a portion of the inner diameter surface 5 b of the cage 5 that faces the non-orbital portion of the inner ring 2.
  • the hair transplant part 6 of (3) and (4) is also arrange
  • all the flocked parts of (3) and (4) are formed continuously or intermittently in the circumferential direction.
  • the other overall configuration is the same as that of the angular ball bearing of the form shown in FIG.
  • the fiber length of the short fiber which comprises the flocked part 6 is single, The length is made into the clearance gap (about half or less of clearance.
  • the gap between the outer ring 3 and the retainer 5 is formed by the flocked part 6 of (1) and (3), and the gap between the inner ring 2 and the retainer 5 is formed by the flocked part 6 of (2) and (4).
  • the bearing rotational speed is low, and when the flocked fiber cannot be expected to spread due to centrifugal force, or when the bearing is stationary, the coolant and foreign matter are prevented from entering the rolling part from each gap. it can.
  • FIG. 4 is a partial sectional view of an angular ball bearing having a flocking portion (outer ring inner diameter surface, cage outer diameter surface, cage inner diameter surface, inner ring outer diameter surface, cage width surface) as an angular ball bearing of the present invention. is there.
  • a flocked portion 6 formed by flocking fibers is formed on the width surface 5c of the cage 5.
  • the other overall configuration is the same as that of the angular ball bearing of the form shown in FIG.
  • the flocked part 6 is also formed on the width surface 5c of the cage 5, the formation region of the flocked part 6 is widened, and more adsorbed coolant liquid and foreign matters that are about to enter from the outside of the bearing, Intrusion into these rolling parts can be suppressed.
  • the flocked portion may be formed not only on the counter bore side but also on the opposite side.
  • a flocked portion that seals the gap between the inner ring 2 and the cage 5 on the opposite side in the axial direction may be formed.
  • the resin cage 5 is made of, for example, a polyamide resin such as a phenol resin, a polyether ether ketone (PEEK) resin, a polyphenylene sulfide (PPS) resin, a thermoplastic polyimide resin, a polyamideimide resin, a nylon 66 resin, or a nylon 46 resin. It is manufactured by injection molding using a resin composition containing a reinforcing fiber such as carbon fiber or glass fiber and other additives as a resin base material. In particular, a phenol resin is preferable because it has a high elastic modulus at a high temperature and can cope with high-speed rotation.
  • a polyamide resin such as a phenol resin, a polyether ether ketone (PEEK) resin, a polyphenylene sulfide (PPS) resin, a thermoplastic polyimide resin, a polyamideimide resin, a nylon 66 resin, or a nylon 46 resin. It is manufactured by injection molding using a resin composition containing a
  • the angular ball bearing of the present invention is not limited to this, and any material such as a metal material can be adopted.
  • the cage type is not particularly limited, and may be a crown-shaped cage or a waveform cage.
  • the flocked portion 6 is formed by flocking short fibers.
  • Spraying or electrostatic flocking can be employed as a flocking method. Even on a curved surface such as the guide surface of the cage, it is preferable to employ electrostatic flocking because a large amount of fibers can be densely and vertically planted in a short time.
  • electrostatic flocking method a known method can be adopted.For example, after applying an adhesive to a range where electrostatic flocking is performed, the short fibers are charged and flocked substantially perpendicularly to the adhesive application surface by electrostatic force, The method of performing a drying process, a finishing process, etc. is mentioned. In addition, electrostatic spraying (fiber coating) can also be employed.
  • the short fiber used for flocking is not particularly limited as long as it can be used as a short fiber for flocking.
  • polyolefin resin such as polyethylene and polypropylene
  • polyamide resin such as nylon, aromatic polyamide resin
  • polyethylene terephthalate Polyester resin
  • polyethylene naphthalate polyethylene succinate
  • polybutylene terephthalate synthetic resin fiber
  • acrylic resin vinyl chloride
  • vinylon (2) inorganic fiber
  • inorganic fiber such as carbon fiber, glass fiber, (3) rayon, acetate, etc.
  • natural fibers such as cotton, silk, hemp and wool.
  • synthetic resin fiber among the above because it is difficult to cause swelling and dissolution with oil, is chemically stable, can produce a large amount of homogeneous fibers, and can be obtained at low cost.
  • the shape of the fiber is not particularly limited as long as it does not interfere with other members that adversely affect the bearing function at the place where the flocked portion is formed.
  • the specific shape is preferably, for example, a length of 0.5 to 2.0 mm and a thickness of 0.5 to 50 dtex, and the density of the fibers in the flocked portion is the ratio of the fibers to the flocked area Is preferably 1 to 40%.
  • the shape of the short fiber there are a straight and a bend (a shape where the tip is bent), and any of them can be used.
  • the adhesive examples include an adhesive mainly composed of urethane resin, epoxy resin, acrylic resin, vinyl acetate resin, polyimide resin, silicone resin and the like.
  • urethane resin solvent adhesive epoxy resin solvent adhesive, vinyl acetate resin solvent adhesive, acrylic resin emulsion adhesive, acrylic ester-vinyl acetate copolymer emulsion adhesive, vinyl acetate emulsion adhesive And urethane resin emulsion adhesives, epoxy resin emulsion adhesives, polyester emulsion adhesives, ethylene-vinyl acetate copolymer adhesives, and the like. These may be used independently and 2 or more types may be used together.
  • the angular ball bearing of the present invention is lubricated with a lubricant (lubricating oil or grease). These lubricants are supplied and sealed in the bearing space between the inner and outer rings, and lubricated by being interposed in the rolling surface. Any lubricating oil or grease can be used without particular limitation as long as it is normally used for an angular ball bearing.
  • the flocked portion as described above is formed, it is easy to fasten the lubricant to the rolling portion. Therefore, for example, even when a low-viscosity base oil or a grease with a high miscibility is used to reduce torque, leakage of the grease or base oil can be suppressed. For this reason, various greases can be widely used.
  • the angular contact ball bearing of the present invention does not require a space in the bearing width direction for sealing, can increase the load capacity, and can suppress the intrusion of coolant liquid or foreign matter. Available for bearings. In particular, it can be suitably used as an angular ball bearing that supports the spindle of a machine tool.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Manufacturing & Machinery (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

L'invention concerne un roulement à billes à contact angulaire qui ne nécessite pas d'espace dans le sens de la largeur d'un roulement pour un joint d'étanchéité, qui permet d'augmenter la capacité de charge et qui peut réduire au minimum l'entrée de liquide de refroidissement et de corps étrangers. Le roulement à billes à contact angulaire 1 supporte un arbre principal de machine-outil ou similaire et est pourvu : d'une bague intérieure 2 et d'une bague extérieure 3 qui sont des bagues de roulement ; d'une pluralité de billes 4 interposées entre les bagues intérieure et extérieure ; et d'un élément de retenue 5 pour retenir les billes 4. La surface de diamètre extérieur 5a du support 5 et une surface de diamètre extérieur 2a de la bague intérieure 2 qui fait face à la surface de diamètre intérieur 5b du support 5 comprennent une section poils 6 dans laquelle les fibres sont implantées en tant que poils. Les sections poils 6 assurent l'étanchéité de l'espace entre la bague extérieure 3 et le support 5 et de l'espace entre la bague intérieure 2 et le support 5.
PCT/JP2016/077500 2015-09-18 2016-09-16 Roulement à billes à contact angulaire WO2017047772A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2015-185318 2015-09-18
JP2015185318A JP2017057986A (ja) 2015-09-18 2015-09-18 アンギュラ玉軸受

Publications (1)

Publication Number Publication Date
WO2017047772A1 true WO2017047772A1 (fr) 2017-03-23

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10883541B2 (en) * 2019-02-19 2021-01-05 Schaeffler Technologies AG & Co. KG Electrically isolated non-sealed bearing

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5540306A (en) * 1978-09-11 1980-03-21 Nippon Seiko Kk Plastic holder
JPS61175200A (ja) * 1985-01-29 1986-08-06 株式会社テクノロジー・リソーシズ・インコーポレーテッド 固体、流体間の界面摩擦抵抗減少方法
JP2014159842A (ja) * 2013-02-20 2014-09-04 Nsk Ltd 転がり軸受
JP2015183725A (ja) * 2014-03-20 2015-10-22 Ntn株式会社 転がり軸受
JP2015194256A (ja) * 2014-03-20 2015-11-05 Ntn株式会社 転がり軸受
JP2016186330A (ja) * 2015-03-27 2016-10-27 Ntn株式会社 転がり軸受

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5540306A (en) * 1978-09-11 1980-03-21 Nippon Seiko Kk Plastic holder
JPS61175200A (ja) * 1985-01-29 1986-08-06 株式会社テクノロジー・リソーシズ・インコーポレーテッド 固体、流体間の界面摩擦抵抗減少方法
JP2014159842A (ja) * 2013-02-20 2014-09-04 Nsk Ltd 転がり軸受
JP2015183725A (ja) * 2014-03-20 2015-10-22 Ntn株式会社 転がり軸受
JP2015194256A (ja) * 2014-03-20 2015-11-05 Ntn株式会社 転がり軸受
JP2016186330A (ja) * 2015-03-27 2016-10-27 Ntn株式会社 転がり軸受

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10883541B2 (en) * 2019-02-19 2021-01-05 Schaeffler Technologies AG & Co. KG Electrically isolated non-sealed bearing

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